Rewind machines



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April 20, 1965 c. AARON ETAL 3,179,349

REWIND MACHINES Filed Nov. 2, 1962 4 Sheets-Sheet 2 INVENTORS Cid/P455 44,?6/1/ am-P4 Pan/0Y4 BY 2/ MM 4.... 5mm.

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rra/PA A'XI April 20, 1965 c. AARON ETAL REWIND MACHINES 4 Sheets-Sheet 4 Filed Nov. 2, 1962 INVENTORS. 644/5465 444v fasvw Pan I74 BY 4 Mam United States Patent 3,179,349 REWIND MACHINES Charles Aaron, West Caldwell, N.J., and Joseph Pundyk,

New York, N.Y., assignors to Cameron Machine Company, Dover, N.J., a corporation of New York Filed vNov. 2, 1962, Ser. No. 234,925 15 Claims. (Cl. 242--65) Thisinvention relates to rewind machines, and more particularly to rewind machines having contact drums and individually driven rewind shafts.

In the usual form of rewind machines, a relatively wide mill or supply web is drawn from a supply roll and is passed partially around several drums which may be driven. Adjacent one of the drums is a plurality of cutters or blades which cut the web into narrower strips or subwebs. The subwebs then pass around a driven drum known as a contact drum, from whence the web passes to rewind shafts on which the web is wound into rewind rolls which bear against said contact drum during the rewinding process. The force exerted between the rewind roll and the contact drum is called the contact pressure or nip force. This force is applied in order to squeeze out the air entrapped between adjacent layers of webbing upon the rewind roll and to prevent the web from slipping sideways or telescoping. Also, during the rewind process rewind torque is exerted upon the rewind roll by the rewind shaft producing tension in the web.

It is important to control the tension exerted upon the web as it builds up upon the rewind roll in order that uniform roll density may be maintained and internal tension may not be excessive. This is particularly important on web materials which have memory. Such materials when Wound on the rewind rolls in a stretched condition, although appearing to .be properly wound, will, upon standing for some time, exert increased tension in the web layers while trying to return to the unstretched condition with the result that the rewind rolls will develop hard and ridged surfaces. On some other materials an excess of rewind tension beyond a light tension will produce hard and ridged rolls while winding.

Heretofore substantial dficulty has been encountered especially when slitting and winding certain type of web materials such as plastics, or the like, which have a tendency to be slippery, or stretchy, or have memory, as previously described, and which are apt to be characterized by varying thicknesses or caliper across the width of Web as well as along the length thereof. Because of such varying web thicknesses certain areas of the web are baggy or longer in the direction of winding while other adjacent areas are taut.

Heretofore, if a multiple number of rewind rolls are rewound with suitable contact pressure applied against a common contact drum, it has been necessary to apply increased rewind torques to those strips which have been slit from baggy sections of the web, in order to overcome the nip force and to cause the strips to be pulled faster than, and to slip ahead of the contact roll surface, thereby taking up the extra length of material. Such increased rewind torques, which are in excess of the normally light rewind torques, are applied by the rewind shaft, and transmitted from the center of the rewind roll outward through the various layers of web in the roll, and tend to produce an undesirably hard and ridged roll.

In view of the foregoing, an object of the present invention is to provide individual contact drums, each of which may be free to rotate at the same surface speed as the respective strip passing thereover. Another object is to provide means whereby the contact pressure and rewind tension are independently controlled for each rewind roll.

Still another object is to provide individually driven re- 3,179,349 Patented Apr. 20, 1965 wind rolls having controlled torque input which is not affected by the nip force on the contact drum. Thus, with our novel concept each individual web strip may be controlled separately. The torque input into the rewind shaft may be controlled so that it will remain nearly constant or be increased as desired as the rewind roll builds up. Because of the use of individual contact drums, torque is applied for winding purposes only. Various means may be employed to impart the torque into the rewind shaft such as hydraulic motors, or the like. Actually, we have found that a clutch produces the desired torque characteristics because the torque can be maintained constant or increased, as desired, over a wide range of speeds.

Since the nip force is isolated and independently controlled in accordance with this invention, it may be readily adjusted without affecting the rewind torque. Separate independent control means may be employed to regulate the nip force, as desired.

Yet another object of this invention is to provide means whereby the contact drum support shaft may be driven, if desired, in order to eliminate the effect of the drag of the contact drum bearings upon the web tension as it passes over the surface of the contact drum.

Another object of this invention is to provide winding means whereby the winding tension in each strip is independently controlled back to the cutters, thus, minimizing the eifect of a loose web area which tends to cause inaccurate width of cut and ragged cut edges.

In order to achieve the aforementioned objectives, we have conceived an effective and practical solution to the problems presented and have actually constructed a successfully operating and commercially desirable rewind machine based upon that concept. In essence, our invention contemplates the provision of a rewind machine comprising a pair of rewind arms pivotally supported at their inner ends and adapted-to support a rewind shaft at their outer ends. A Web of sheet material is wound into a rewind roll about the rewind shaft. Means is provided at the outer end of one of the arms for driving engagement with the rewind shaft and preferably is adapted to produce controlled torque output. Such means may include a clutch having the driving side thereof connected to the rewind shaft and its driven side connected to an electric motor, an air motor, a driven cross shaft, or the like. Control means for the clutch are provided for regulating the input torque to the rewind roll. Actually, it may be desirable to maintain the input torque substantially constant or with an increase thereof while the rewind roll diameter increases, depending upon the requirements of the material being wound.

A contact drum is provided which is adapted to be in peripheral engagement with the rewind roll. The contact drum may have a frictioned peripheral surface thereon over which the web passes toward the rewind roll. In the present embodiment said contact drum is rotatably mounted on anti-friction hearings on a contact drum support shaft. Means may be provided for rotating said support shaft so that when the surface speed of the contact drum is substantially equal to the linear speed of the web feed, there is no appreciable rotation of bearing balls in the races and even the slight bearing friction is practically eliminated.

The invention in a form thereof contains a front pair of rewind arms and corresponding contact drum as well as a rear pair of rewind arms and corresponding contact drum. The invention in a further form thereof contains a plurality of linearly spaced front pairs of rewind arms and contact drums as well as a plurality of linearly spaced rear pairs of rewind arms and contact drums. It is noted that one contact drum is provided for each pair of rewind arms. However, a plurality of front contact drums may be rotatably mounted about the same contact drum support shaft, and similarly a plurality of rear contact drums may be rotatably mounted about a second contact drum support shaft.

Further objects, features and advantages of the'invention hereof will appear from the following detailed description given below taken in connection with the accompanying drawings which form a part of this specification and illustrateby way of example, preferred embodiments of the invention.

In the drawings:

FIG. l is a side elevation showing onejembodiment of a rewind machine constructed in accordance with this invention;

FIG. 2 is a perspective view illustrating the rewind shaft'and arms assembly;

FIG. 3 is a sectional view taken along the line 3--3 of FIG. 1; and

FIG. 4is a sectional view taken along the line 4-4 of FIG. 1 andshowing details of the construction of the contact drum support shaft and contact drum assembly.

Referring now to the drawings and particularly to FIG. 1 thereof, there is illustrated a duplex rewind machine which comprises a 'front portion designated generally at 6 and a rear portion designated generally at 8. A supply roll '10 comprising material which is to be rewound is mounted on a supply roll shaft 12 in suitable proximity to the remainder of the rewind machine. A

web 14 is led from the supply roll 10 over an idler roll 16 around a cutting roll 18 and another idler roll 26. The idler rolls 16 and 20 and the cutting roll 18 may, if de sired, have torque applied to their center shafts 17,19 and 21, respectively, if desired, in order to minimize the tension developed in the web when passing thereover. Slitters or cutters 22 are provided adjacent the cutting roll 18 to cut the web into strips or subwebs of the desired rewind widths as the web passes thereby. From the idler roll 20 the web is led to the contact drums 24 and 236. Contact drum 24 is part of the front rewind assembly while contact drum 2 6 is part of the rear rewind assembly. The web strips as they leave the idler roll 20 are led alternately to the contact drums 24 and 26 for a purpose which will be described more fully hereinafter. The contact drums are each rotatably mounted about contact drum support shafts 32 and 34, respectively. The extremities of the support shafts are eachsuitably journaled in bracket 36, an electric motor 31 may be employed to drive the support shaft, if desired. Bearing clamp 38 with bearing clamp bolts 40 is illustrated as a means for clamping the ends of the shafts 32 and 34 within the bracket 36. Bolt holes 42 are provided as a convenient means for securing the bracket 36 to the rewind machine frame assembly (not shown).

It is noted that idler roll 20 is positioned in fixed spaced relationship relative to the contact drum support shafts 32 and. 34 during the complete rewind cycle of operation. Thus, the linear distance that the web 14 must travel after leaving'the idler roll 20 and before engaging the contact drum 24 or 26 is held to a minimum. This provides accurate and consistent tracking or passage of the web 14 thereby.

Front and rear rewind rolls 33 and 35 are illustrated in peripheral engagement with their respective contact drums :24 and 26. Thus, the individual strips of Web 14 are led from contact drums 24 and 26 to their corresponding rewind rolls 33 and 35. It is noted that the various rolls and contact drums rotate in the directions indicated by their respective arrows as shown in FIG. 1.

Referring now to FIGS. 2 and 3, there is illustrated in greater detail the front portion 60f 'a rewind machine constructed in accordance with this invention. The rear portion 8 of the rewind machine is constructed and operates in substantially the same manner as the front portion so that the following description is equally applicable thereto. A rewind shaft .44 is suitably mounted in bearings 46 which are contained in the rewind arms 47 and 48. The rewind shaft 4-4 is provided with rewind chucks 50 which in turn support the rewind core 52. Rewind chucks 50 are removable from and adjustably positioned on rewind shaft 44. One strip of web 14 is led from the contact drum 24 to the rewind core 52 where it forms a rewind roll 33 thereabout. The space between the rewind arms 47 and 4-8 may be increasedor decreased in order to accommodate various lengths of rewind shafts 44. Also chucks 59 may be positioned on shaft 44 to utilize all or part of the usable length of shaft 44. Thus, a suitable rewind core length may be selected for any particular rewind web width.

Bearing clamps 56 and bearing clamp plate 58 co-act to maintain the rewind shaft 44 within suitable axial alignment and to reduce the shaft end play to a minimum.

Covers 60 are provided in order to enclose the bearings 46 in an appropriate manner.

In the preferred embodiment the rewind shaft 44 is driven by a clutch member designated generally at 62 through a pair of mating gears 64 and 66. Gear 64 is mounted upon rewind shaft 44 while gear 66 is mounted upon a drive gear shaft 68 and. secured in place thereon by means of clamp plate 70 which is held by machine screw 71. The drive gear shaft 68 is. mounted in the rewind arm 47 by means of duplex bearings '72. Bearing retainer plate 74 maintains the bearings .72 in axial alignment within the rewind arm 47.. Rewind drive pulley 76 is indirectly mounted upon drive gear shaft 68 through bearings '78 which are prevented from excess axial movement by means of snap ring 8! and pulley flange 81. The clutch 62 further comprises friction material support plate 82 and friction material83. Pressure cover 84 is slidably keyed to the drive gear shaft 68 by means of key 35 and thereby positively rotates with same. The face of pressure cover 84 is adapted so that upon axial movement thereof it is urged into sliding frictional engagement with the friction material 83. Pressure cover 84 may be provided with breather holes 86 for cooling purposes, if desired.

Pressure roller lever 88 pivots about pin 99 which is mounted in a U-shaped block 92. Block 92 is fixedly secured to the rewind arm 47. At one end of the pressure roller lever 88 is a U-shaped portion 89. Rollers 94 are rotatably mounted at the extre'm-ity of the U-shaped portion 89. Nuts 96 acting in conjunction with pins 97 are employed to secure the rollers 94, as shown. The rollers 94 are adapted to engage the pressure cover 84 and urge same in an axial inwardly direction. When the pressure cover 84 is urged towards the left as viewed in PEG. 3, then the pressure cover 84 will tend to engage the friction material 83 with more pressure and thereby the pulley '76 will tend to drive the drive gear shaft 68 with an increased torque. Conversely, when the pressure of the rollers 94 engages the pressure cover 84 with less force, the torque will be decreased, and the drive gear shaft 6% will transmit a reduced torque. The other end of the pressure roller lever 88 is adapted for engagement with a piston rod 93 which protrudes from the singleaoting air cylinder 160. The air cylinder is fixedly mounted upon the rewind arm 47. Air is supplied under controlled pressure to one end of the air cylinder 1% through hose 182 from an air supply cylinder 164. Thus, when the air pressure is increased the piston rod 98 urges one end of pressure roller lever 88 outwardly. Since pressure roller. lever 88 pivots about pin 90, the other end or U-shaped portion 89 moves inwardly and rollers 94 urge pressure cover 554 inwardly with greater force. The air supply cylinder 3W4 which controls the aforementioned pressure exerted or torque transmitted in the clutch mechanism 62 may readily be controlled manually by the operator because a relatively constant air pressure will maintain a substantially constant torque input into the rewind shaft 44. In lieu thereof any commercially available constant pressure air supply regulator may be utiiized if desired.

Drive pulley 106 is keyed to the air motor shaft 108. A toothed or V-belt 114 is interposed between the drive pulley 106 and the rewind :drive pulley 76. Air motor 116 is fixedly secured to the rewind arm 47 by means of bracket 118 and bolts 120. The air motor 116, which preferably has a variable speed, is actuated by air under pressure which is supplied via hose 122 from an air supply source 124. The air supply source 124 for the air motor 116 may be maintained at a constant pressure or it may be manually adjusted, if desired. It is noted that in lieu of the air motor illustrated any other convenient motive means may be employed such as an electric motor, a hydraulic motor, or drive pulley 106 may be interconnected with a central rewind machine motor via a cross shaft and appropriate gearing, for example. The air motor drive is more advantageous than a hydraulic motor as there is no possibility of leakage with its resultant contamination as might be incurred with the use of a hydraulic system. A variable speed motive means is preferable because it tends to reduce the heating and frictional wear of the clutch mechanism.

The inner ends of the rewind arms 47 and 48 are fixedly connected to the lever support shaft 126. In order to vary the spacing between the two rewind arms 47 and 48 for the purpose mentioned heretofore, lever support shaft 126 comprises two sections 128 and 130. Interposed between the two sections is a coupling shaft 132 which may be provided in various lengths. Coupling members 134 are utilized to interconnect the coupling shaft 132 with its adjacent lever support shaft sections 128 and 130. The lever support shaft 126 is pivotally mounted in bearings 136 (one set being shown) which are contained in lever support brackets 138 and 140. Cap member 139, secured in place by bolts 141, restricts the axial movement of lever support shaft 126. Such support brackets 138 and 140 each contain a stationary arm 139 and 141,

respectively. Double-acting air cylinder 142 is pivotally connected to rewind arm 47 by means of a pin 144 passing through lug 146 provided for the purpose. A piston rod 148 extends from the opposite end, of air cylinder 142 and is fixedly secured to a yoke 150. The yoke 159 is pivotally secured to the stationary arm 141 by means of pin 152. Air under controlled pressure is supplied to each end of air cylinder 142 via hoses 156 and 158 which are led from air supply cylinders 157 and 159, respectively. Interposed between rewind arm 47 and lever support bracket 140 is a second double-acting air cylinder 154 which is constructed and operates in substantially the same manner as air cylinder 142 just described. Air is like-wise supplied to air cylinder 154 via hoses which are led from an air supply cylinder (not shown). The rewind contact pressure applied through the rewind arms 47 and 48 is controlled by means of varying the air pressure supplied to the air cylinders 142 and 154. The control of the air pressure supplied may be provided by suitable means known to those skilled in the art such that the nip force between the contact drum 24 and the rewind roll 33 may be maintained at a preselected amount throughout the rewind cycle. In other words, the increasing weight of the rewind roll as the rewind roll builds up or increases in diameter during the rewind process may be compensated for by adjusting the pressure to air cylinders 142 and 154. For example, apparatus suitable for this purpose is disclosed in US. Patent 2,872,126 granted February 3, 1959. If desired, the operator may manually adjust the air pressure to obtain the desired results.

The lever support brackets 138 and 140 are longitudinally slidably mounted upon a set of ways 160. Set screws 162 are provided to secure the lever support brackets 138 and 140 to the ways 160 at a preselected distance apart.

Re-ferring now in particular to FIG. 4, contact drum 24 and contact drum support shaft 32 are shown in greater detail. A plurality of contact drums (two being shown) 24 and 164 are freely rotatably mounted about a single contact drum support shaft 32 by means of antifriction bearings 166. The contact drums are provided with shoulders 168 which maintain the bearings in spaced relationship one to the other as determined by the length of the contact drum which in turn is determined by the maximum width of the strip being rewound. Locking nuts 170 are interposed between the contact drums 24 and 164 and serve to maintain the hearings in proper axial relationship one to the other as shown. Rewind drums 24 and 164 may be spaced apart so that their respective locking nuts 170 are not in contact with each other. It is noted that driving means (not shown) may be employed for driving the contact drum support shaft 32. Such means may include a gear keyed thereto and driven by the main rewind machine motor, for example. The rotational speed of the contact drum support shaft should be maintained substantially equal to the rotational speed of said contact drum in order to minimize the bearing frictional loss between the shaft and drum. The outer surface 172 of the rewind drums may be a frictioned surface which improves the tracking of the web when passing thereover and thus enhances the rewind pattern. Such surface material may include rubber, cork composition, or the like.

As previously discussed, the web strips as they leave the idler roll 20 are led alternately to the contact drums 24 and 26. One individual contact drum, one individual rewind roll and a pair of rewind arms is utilized for each web strip. One strip of webbing is led to the front portion 'of the rewind machine and the next adjacent strip of webbing is led to the rear portion of the rewind machine in order to provide space for the rewind arms and the individual contact drums.

. Although a single front portion 6 and a single rear portion 3. are illustrated in the drawings, a plurality of groups may be employed if desired. That is a plurality of rewind rolls similar to 33 may be positioned in horizontal linear spaced relationship one to the other. A pair of rewind arms and an individual contact drum are required for each rewind roll. Support brackets similar to those designated as 138 and 140 are required for each pair of rewind arms and are all mounted on the same set of Ways 160. Further, a plurality of contact drums may all be rotatably mounted about the same contact drum support shaft 32, two contact drums 24 and 164 being illustrated in FIG. 4. Likewise, a corresponding plurality of rewind rolls may be provided in the rear portion of the rewind machine. It is noted that many strips of webbing may be cut at the same time and also they may be of different widths, as desired. Also the air pressure to contact pressure cylinders 142 and 154 and to clutch air cylinder may be separately controlled for each pair of rewind arms. This may be desirable when a plurality of rewind rolls of varying widths are being wound at the same time either in the front or the rear sections.

As heretofore described, the individual web strip may be narrower than the maximum width which can be accommodated on a given size of rewind shaft 33. Likewise, the strip on each contact roll 24 and 164 illustrated may be narrower than the surface of said contact drums because of the space provided by alternation of the strips to the front and rear sections of the rewind machine. Therefore, one width of contact roll will suffice for a range of widths. As required, other widths of contact rolls may readily be positioned on support shaft 32.

Also, the invention is not limited to a pair of rewind arms, such as 47 and 48 for supporting a rewind roll, but a single arm may be employed in lieu thereof and each rewind shaft may be mounted thereon in cantilever fash- 1011.

Although certain particular embodiments of the invention are herein disclosed for purposes of explanation, further modifications thereof, after study of this specification, will be apparent to those skilled in the art to which the invention pertains. 7 Reference should accordingly be had to the appended claims in determining the scope of the .invention.

What is claimed and desired to be secured by Letters Patent is:

1. In a rewind machine, the combination of a front group and a rear group, each group comprising a plurality of pairs of rewind arms each pair pivotally supported at their inner endsv and adapted to support a re .wind shaft at their outer ends on which shaft a strip vof sheet material is to be wound into a rewind roll, one .of said arms of each pair carrying at its outer end means for centerdriving engagement with saidshafhindividual motive means drivingly connected .to each of said means .for driving engagement, a contact drum support shaft, a plurality of contact drums freely rotatably mounted on said shaft independently each from the other, at least one of said contact drums being .provided for each of said rewind rolls, and said contact drums adapted for peripheral engagement with their corresponding rewind rolls and being provided with peripheral surfaces thereon over which said strips passtoward said rewind rolls.

2. The rewind machine in accordance with claim 1 wherein said motive means have constant torque output.

3. The rewind machine in accordance with claim 1 wherein said contact drums are provided with frictioned peripheral surfaces.

4. The rewind machine in accordance with claim 1 .wherein means are provided for driving said contact drum support shaft.

5. The rewind machine in accordance with claim 1 wherein means are provided for controlling the contact pressure between said contact drums and their respective rewind rolls. i

6. In a rewind machine, the combination 'of a front group and a rear group, each group comprising a plurality of pairs of rewind arms each pair pivotally supported at their inner ends and adapted to support a rewind shaft at their outer ends on which shaft a strip of sheet material is to be wound into a rewind roll, one of said arms of each pair carrying at its outer end means for center driving engagement with said shaft, individual motive means drivingly connected to each of said means for driving engagement providing torque input to each of said shafts, means for controlling the torque input to each of said shafts, a contact drum support shaft, a plurality of contact drums freely rotatably mounted on said support shaft independently each from the other,

at least one of said contact drums being provided for each of said rewind rolls, said contact drums adapted for peripheral engagement with their corresponding rewind rolls, and said contact drums having peripheral surfaces thereon over which said strips pass toward said rewind rolls.

7. The rewind machine in accordance with claim 6 wherein said contact drums are provided with frictioned web material in the form of a rewind roll, one of said arms of each pair carrying at its outer end means .for center driving engagement with said shaft, individual motive means drivingly connected to each of said means for driving engagement providing torque input to each of said shafts, control means for said motive means for maintaining the torque input to each of said rewind rolls substantially constant while its diameter increases, a contact drum support shaft being provided for each group, an idler roll being positioned in fixed spaced relationship to said contact drum support shafts, a plurality of contact drums independently, freely rotatably mounted on each of said shafts, at least one of said contactdrums being provided for each of said rewind rolls, said con tact drums adapted for peripheralengagement with their corresponding rewind rolls, said contact drums and said idler roll being provided with a peripheral surface thereon over which said strips pass toward said rewind rolls, means for driving said contact drum support shafts so that their rotational speeds are substantially equal to the rotational speeds of said drums respectively, and

means for individually controlling the contact pressure between said contact drums and their respective rewind rolls.

11. In a rewind machine, the combination of a front group and a rear group, each group comprising a pair of rewind arms pivotally supported at their inner ends and adapted to supporta rewind shaft at their outer ends on which shaft a strip of sheet material is to be wound into a rewind roll, one of said arms carrying at its outer end means for center driving engagement with said shaft, a clutch having the driven side thereof drivingly connected to said means for driving engagement, motive 'means having its power output drivingly'connected to the driving side of said clutch providing torque input to said shaft, means for controlling said clutch, a contact drum support shaft, a contact drum freely rotatably mounted on said shaft and being in peripheral engagement with said rewind roll, said contact drum having a peripheral surface thereon over which said web passes toward said rewind roll.

12. In a rewind machine, the combination of a front group and a rear group, each group comprising a plurality of pairs of rewind arms each pair pivotally supported at their inner ends and adapted to support a rewind shaft at their outer ends on which shaft a strip of sheet material is to be wound 'intoa rewind roll, one of said arms of each pair carrying at its outer end means for center driving engagement with said shaft, a clutch for each rewind roll having the driven side thereof drivingly connected to said means for driving engagement, individual motive means drivingly connected to the driving side of said clutches, control means for each of said clutches, a contact drum support shaft, a plurality of contact drums freely rotatably mounted on said shaft independently each from'the other, at least one of said contact drums, being provided for each of said rewind rolls, said contact drums adapted for peripheral engagement with their corresponding rewind roll and being provided with a peripheral surface thereon over which said web passes toward said rewind roll, and means for driving said contact drum support shaft so that its rotational speed is substantially equal to the rotational speed of said drums.

13. The rewind machine in accordance with claim 12 wherein means are provided for individually controlling the contact pressure between said contact drums and their respective rewind rolls.

14. The rewind machine in accordance with claim 12 wherein means are provided for controlling said motive means.

15. In a rewind machine, the combination of a plurality of independently mounted rewind shafts divided into a rear group and a front group, a pair of rewind arms being provided for each rewind shaft, each of said rewind shafts being adapted for the winding thereon of web material in the form of a rewind roll, one of said arms of each pair carrying at itsouter end means for center driving engagement with said shaft, a clutch for each rewind roll having the driven sidethereof drivingly connected to said means for driving engagement, individual motive means drivingly connected to the driving side of each of said clutches providing torque input to each of said shafts, control means for said clutches for controlling the torque input to each of said shafts, control means for said motive means, a contact drum support shaft being provided for each group, a plurality of contact drums independently, freely rotatably mounted on each of said shafts, at least one of said contact drums being provided for each of said rewind rolls, said contact drums adapted for peripheral contact with their corresponding rewind roll and being provided with a peripheral surface thereon over which said web passes toward said rewind roll, means'for driving said contact drum support shafts so that their rotational speeds are substantially equal to the rotational speeds of said drums contact pressure between said contact drums and their respective rewind rolls.

References Cited by the Examiner UNITED STATES PATENTS 716,923 12/02 McKean 24265 2,020,118 11/35 Kellet et a1. 24265 2,460,694 2/ 49 Haswell 242----5 6.4 2,777,644 1/57 Nicholson 242-65 2,872,126 2/59 Rockstrorn et a1 24265 2,985,398 5/61 Rockstrom et al 24265 3,086,726 4/63 Aaron 24265 MERVIN STEIN, Primary Examiner.

respectively, and means for individually controlling the 15 DONALD W. PARKER, Examiner. 

1. IN A REWIND MACHINE, THE COMBINATION OF A FRONT GROUP AND A REAR GROUP, EACH GROUP COMPRISING A PLURALITY OF PAIRS OF REWIND ARMS EACH PAIR PIVOTALLY SUPPORTED AT THEIR INNER ENDS AND ADAPTED TO SUPPORT A REWIND SHAFT AT THEIR OUTER ENDS ON WHICH SHAFT A STRIP OF SHEET MATERIAL IS TO BE WOUND INTO A REWIND ROLL, ONE OF SAID ARMS OF EACH PAIR CARRYING AT ITS OUTER END MEANS FOR CENTER DRIVING ENGAGEMENT WITH SAID SHAFT, INDIVIDUAL MOTIVE MEANS DRIVINGLY CONNECTED TO EACH OF SAID MEANS 